CA1197438A - Four way valve with internal pilot - Google Patents
Four way valve with internal pilotInfo
- Publication number
- CA1197438A CA1197438A CA000440343A CA440343A CA1197438A CA 1197438 A CA1197438 A CA 1197438A CA 000440343 A CA000440343 A CA 000440343A CA 440343 A CA440343 A CA 440343A CA 1197438 A CA1197438 A CA 1197438A
- Authority
- CA
- Canada
- Prior art keywords
- spool
- pilot
- valve
- ports
- axially
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000012530 fluid Substances 0.000 claims abstract description 100
- 230000007935 neutral effect Effects 0.000 claims abstract description 58
- 238000007789 sealing Methods 0.000 claims abstract description 28
- 230000033001 locomotion Effects 0.000 claims description 20
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 230000005294 ferromagnetic effect Effects 0.000 claims description 2
- 230000000712 assembly Effects 0.000 claims 2
- 238000000429 assembly Methods 0.000 claims 2
- 230000000694 effects Effects 0.000 abstract description 11
- 230000007246 mechanism Effects 0.000 description 9
- 230000009471 action Effects 0.000 description 3
- 230000004044 response Effects 0.000 description 2
- 229940000425 combination drug Drugs 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000009699 differential effect Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 230000005291 magnetic effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
- F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
- F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86582—Pilot-actuated
- Y10T137/86606—Common to plural valve motor chambers
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86582—Pilot-actuated
- Y10T137/86614—Electric
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Multiple-Way Valves (AREA)
- Fluid-Driven Valves (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A four-way valve for selectively controlling the application of fluid and exhaust pressures to opposite sides of a double acting cylinder utilizes a main valve spool that is axially movable in a valve housing defining ports respectively connected to opposite sides of the cylinder and to the pressured and inlet sides of a fluid pressure source. The spool valve is provided with an axial bore and a pilot spool is mounted in such axial bore.
Radial passages are provided in the main valve spool connecting its exterior with the axial bore and external sealing portions on the pilot spool cooperate with the radial port so that in a neutral position of both the main valve spool and the pilot spool, no fluid flow occurs.
Upon axial shifting of the pilot spool in either direction from the neutral position, fluid pressure is applied to opposite ends of the main valve spool to cause it to follow the pilot spool and thus effect a connection between the outlet and inlet ports of the fluid pressure source and the appropriate side of the double acting cylinder.
A four-way valve for selectively controlling the application of fluid and exhaust pressures to opposite sides of a double acting cylinder utilizes a main valve spool that is axially movable in a valve housing defining ports respectively connected to opposite sides of the cylinder and to the pressured and inlet sides of a fluid pressure source. The spool valve is provided with an axial bore and a pilot spool is mounted in such axial bore.
Radial passages are provided in the main valve spool connecting its exterior with the axial bore and external sealing portions on the pilot spool cooperate with the radial port so that in a neutral position of both the main valve spool and the pilot spool, no fluid flow occurs.
Upon axial shifting of the pilot spool in either direction from the neutral position, fluid pressure is applied to opposite ends of the main valve spool to cause it to follow the pilot spool and thus effect a connection between the outlet and inlet ports of the fluid pressure source and the appropriate side of the double acting cylinder.
Description
3~
The invention relates ~o a four-way spool type valve for controlling the respective application of fluid pressure and ~xha~st pressure to opposite sides of a double acting piston disposed within a cylinder r wherein the pilot valve for controlling the moveme~s of the v~lve spool is contained within an axial bore extending through the valve spool.
A four-way hydraulic valve or the selective application of fluid pressure and exhaust pressure xespectively to opposite sides of ~ double acting piston-cylinde.r combination has been heretofore utiliz.ed in many industrial applications. Where substantial fluid pressures are invol~ed, the four-way valve generally has to be of substantial si2e in order to withstand the pressures applied to the double acting cylinder. Such control valve has generally taken the form of an outer housing containing axially spaced radial ports which are ~espectively connectable to the pressure and exhaust side of a fluid pressure souxce and the opposite sides of th~ cylinder containing the double acting piston. The flow of fluid through the proper ports is norn~ally controlled by an axially shiftable spool mounted within the ported housing and having external sealing elements for effecting the required separation of the various ports in accordanc~ with the ax.ial position of the spool relative to such ports~ To effect the xapid shifting of the valve spool in order to expedite the application of proper control pressures to the double acting cylinder, it has been common to apply diferentlal fluid pressures to the ends of the spool through th~ m~dium of a relatively small pilot valve ? which .~ ~
is operated either manually or hy an el.ectrical or hydraulic actuator. The employment o a separate pilot valve inherent-ly involves the utilization of separate fluid pressure con--duits leading from the pilot valve to the main spool type valve, with an attendant increase in total bulk of the val-ving packagef increased cost of assembly, arld increased risk of failure of the valve du0 to rupture of the exposed ex-~ernal piping.
There is a need, there~ore, for a four-way spool type hydraulic valve employing a pilot valve to efect -the control movements o~ the spool of the four-way valve~ where-in the pilot valve may be incorporated as an internal part of the spool valve and any external conduits connecting the pilot ~alve to the spool valve may be elimlnated.
Moreover, there is often a need for convenient adjustment of the speed of operation of a double acting cv-linder controlled by a four-way spool valve.
Accordingly, the lnvention provides a ~al~e for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamb~r incorporating a fluid pressure responsiva piston, comprising, in combina-tion, a hollow housing having an axially spa~ed pair of first radial ports Gonnectable respectively to the fluid pressure chamber on opposite sides o~ the piston, an axially spaced pair of second radia~ ports connectable respectively with the inlet and outlet of the fluid pressure source, the first ports being respectively axially adjacent the second ports, a valve spool axially slidable in the bore of -~he hollow housing, the valve spool hav.ing axially spaced external seal elements cooperable with the housing bore and recessed ex ternal surfases intermediate the external seal elements, whereby in a neutral axial position of the spool no fluid flow occurs~ in one axial position of ~he spool away Erom the neutxal position, pressurized fluid flows through the pair of first ports in one direction, and in a second axial position of the spool in the opposite direction from the neutr~l position the flow of pressurized fluid through the r~
3~1 2a pair of first ports is r~versed, the valve spool having an axial bore and radial ports connecting the valve spool bore with the recessed external surfacesl a pilot spool axially shiftably mounted in the valve spool bore, external sPaling means on the pilot spool respectlvely sealing each of the radial ports in a neutral position of -the pilot spool rela-tive to ~he valve spooll a pair of axially extending pass-ages r~spectively exte~diny rom ~ region intermediate -the external sealing means on th~ pilot spool to an axial end region of the hollow housing, and means ~or axially dis-placing the pilot spool from its said neutral position, thereby applying pressured fluid to one end of the valve spool to axially shi~ same from its said neutral positionO
The invention contemplates the provision of an axial bore in the spool of an otherwise conventional Eour way hydraulic spool valve. Within such axial bore, there is slidably mounted a pilot spool element. One end of the pilot spool element extends axially out of the valve spool bor~ and is connected to means Eor eEfecting an axial dis-placement of the pilot spool relative to the main valve spool.Such means may, or example, comprise a pa~r of solenoids surrounding a magnetic core element which is secured to the pilot valve so that selective energization of one of the ~olenoids effe¢ts the shifting of the pilot spool in one or ths other axial direction.
A plurality of radial ports are provided in the main valve spool respectively connecting the valve spool bore with two conduits in the main valve housing which are connectea to the return side of the hydraulic pressure 3~
source and with a single conclui~ connected to the pressure side of the hydraulic pressure source. The pilot spool is provided with a~ially spaced sealing shoulders which, in the neutral position of the pilot spool relative to the main valve spool, respective]y close each of the radial ports in the main valve spool. The pilot spool is noxmally held in such neutral position by a centering spring.
Axial displacement of the pilot spool by the external means provided for such purpose effects the connection of the fluid pressure conduit to one and of the main valve spool and the exhaus-t or return fluid conduit to the other end of such spool. Such fluid pressure differential effects a shiftin~ of the ma:Ln spool to effect the connectioll of one side of the double acting cylinder controlled by the four-way valve to the pressure source while the other side is connecked to the exhaust or return fluid conduit, hence effecting the actuation of the double acting cylinder. Such movement of the main spool valve constitutes an exact following movement ~f the shifting of the pilot spool so that these two elements again resume a neutral position relative to each other where the fluid pressures on the opposite ends of the main valve spool are again balanced, and the main valve spool remains in its described energi~ing conditi~n until the pilot spool is shifted in the opposite directlon by its actuating means.
~ 'he movement of the pilot spool past its neutral position in an opposite dirertion effects a reversal of the application of f1uid pressure and exhaust pressure xespectively to the opposite ends of the main valve spool, and thus shifts the main val-~e spool in a dir~ction opposite to that previously ~escribed. Such axial shifting movement of the main valve spool reverses the application of fluid pressure and exhaust pressure to the sldes of the double acting cylinder and thus effects a reversal of the operation of such cylinder. Again, -the movement of the main valve spool exactly follcws the movement of the pilot ~7~
valve and it again assumes the neutral position with respect to the pilot valve wherein the ~luid pressure operating on the ends of the main valve spool are equali~ed.
Whenever the actuatins force is removed from ~he pilo-t spool, the pilot spool r~turns to its original neutral posi-tion through the action of the centering spring, an~ the spool of the our-way valve is returned to its initial posi-tion wherein no fluid pressure is applied to the double acting cylind~r controlled by such valve.
The fact that the main spool exactly follows the axial movements of the pilot spool p~rmits a throttling action to he imposed on fluid flow to the controlled cylinder sim-ply by adjusting the limits of movement of the pilot spool.
Further objects and advantages of the invention will be readily apparent to those skilled in the art from the following detailed description, taken in conjunction with the annexed sheets of drawings on which is shown a preferred embodiment of the invention.
Embodiments of the invention will now be described, by way of example, with reference to the accompanying draw-in~s in which:
Figure 1 is a vertical sectional view of a four-way hydraulic valve incorporating an embodiment of this invention, with the elements of the valve shown in their neutral or de-energizing positions.
Figure 2 is an enlarged scale view of a portion of Figure 1, buk illustrating the position of the pilot spool when it is axially shifted in one direction by the actuating solenoîd.
Figure 3 is a view similar to Figure 2 bu~ illustra-ting the position ass~uned by the maln valve spool in response to the axial shifting of the pilot spool.
Figure 4 is a view similar to Figure 3 but showing the positions assumed by the pilot spool and the main spool valve in response to an actuation of the pilo-t spool in an opposite direction.
'~
7~3~
Figure 5 is a fragmerl~ary elevational view of the ported portion 3f the valve sleeve housing.
Keferring to Figure 1, there is shown a complete four-way spool type valve 1 embodying this invention. Such valve comprises an outer main housing 10 defining a central bore 11 which is open only at one end. Housing 10 is provided wi~h a plurality of axially spaced radial port~
10 12, 13, 14, 15, 16 and 17, each extending from the periphery of the housing 10 into communication with the bore 11. Each port i5 internally threaded to receive a correspondingly threaded end of a conduit in the case o~
ports 12 through 16, and to receive a plug in -the case o~
port 17.
Ports 15 and 16 are respectively adapted for connection to opposite ends of a conventional double acting cylinder~ (nQt shown) i.e., a cylinder ha~ing a piston medially disposed therein and fluid pressure chambers disposed on each side of such piston so that the application of a fluid pressure differential -to opposite sides o the piston produces a cor.responding movemPnt of the piston in the cylinder. Port 13 is ~dapted for connection to the pressured outlet side of a fluid pressure source ~not shown) an~ ports 12 and 14, which are respectively axially spaced on oppos~te si.des of port 13 are adapted for connection to the return or inl~ of the fluid pressure source. Port 17 is located adjacent the extreme innex end of the housing bore 11 and is provided solely for the purpQse of dxaining the val~e 1 by removal of a plug therefrom ~not shown)O
While the housin~ 10 could be employed alon~ ~o directly mount an axially reciprocable valve spool 20 therein, this invention preferably utilizes an intermediate sleève housing 18 which is fixedly and sealably mounted within the bore 11 of the outer housing 10~ Sleeve 18 may 3~3 thus be economically fabric~te~ from a metal having better anti-friction characteristics for the mounting of the main valve spool 20 therein. Valve sleeve 18 is provided with radial ports 18a, 18b, 18c, 18d, and 18e respectively alisn`able with the ports 12, 13, 14, 15, and 16 provided in the main valve housing 10. O-ring seals 19 ~Fig~ 5) are mounted in clrcular slots cut around the exterior perimeter of the res~ective ports 18a-18e to effect a sealing engagement between bore 11 of the outer valve housing 10 and the inner sleeve housin~l 18. Sleeve housing 18 is secured in its inserted posi.tion in ~he main housing bore 11 by a plate 9 which is cer,trally apertured to abut a shoulder 18 f provided on the sleeve housing 18 and is secured to the end face of t:he main valve housing 10 by one or more bolts 9a. An O-rincl seal 18g is mounted in the outer end of sleeve housing lB and effects a further seal between the sleeve housing 18 and the bore 11 of the main housing 10.
Within the polished bore 18h ~f the housing sleeve 18, there is mounted a valve spc~ol 20 for axially slidable movements. Spool 20 is provided with axially spaced external sealing shoulders ~'1, 22, 23 and 24. Between the adjacent shoulders the exte~-nal surface of the valve spool is recessed, as indicated al 21a, 22a, and 23aO In a neutral or inoperative posil:ion of the valve spool 20 with respect to the ports 12 through 16, the sealing shoulders are disposed so as to isolal:e the various ports from each other and prevent all fluid flow through the valve 1 to the controlled cylinderO The annular recesses 21a, 22a, and 23a are in turn respectivel~y connected to a ~ore 20a extending through the valve spool 20 by a plurality of radial ports 25, 26 and 27.
The extent of axial di:placement of valve spool 20 relative to housing sleeve :L8 is respectively limited in each direction by annular seal structures 28 and 29 which are respectively held in a :~ix~d position within the bor~
.
3~
18h of housiny sleeve 18 by ('-rings 28a and 29a respectively.
In accordance with this invelltion, a pilot spool 30 is mounted for axial movements within the axial bore 20a of the spool v~lve 20 and is sealingly eng~ged by seal elements 28b and 29b provid~d in the annular seal structures 28 and 29. Pilot spool 30 is provided with ~xially spaced sealing portions 31~ 32 and 33, which, in the neutral position of the pilot spool 30 relative to ~he valve spool 20 are respectively disposed in overlying relationship to the radial ports 25~ 26 and 27 when the pi.lot spool 30 is disposed in a neutral position with respect to the main spool valve 20. External recesses 31a and 32a are formed intermediate shoulders 31~ 32 and 33.
Pilot valve 30 is held in the aforesaid neutral positi.on by a centering spring mechanism 40 comprising an annular housing 41 which is externally threaded into internal threads 18k pLovided in the end of the housing sleeve 13. The spring centering housing 41 defines two axially spaced internally projecting shoulders 41a and 41b which respectively define stops for annular spring seats 42 and 43, which are in abuttment with C-rings 44 and 45 secured to the pilot spool 30. A spring 46 between spring seats 42 and 43 resiliently maintains the pilot spool 30 in its afores~id neutral position relative to the main valve spool 20.
In the neutral position of the pilot spool 30, a pair o:E generally U-shaped fluid passag~s 30a and 30b provided in the body of the pilot spool 30 respectively extend from a position axially inward from the recessed poxtions 31a and 32a of the pilot spool 30 to two outlets on the pilot spoGl which are respectively disposed within enlarged counter bores 20c and 20d provided .in the ends of the bore 20a of the valve spool 20.
The end of the valve spool 30 projecting axi~lly beyond the centering spring mechanism 40 is secured, as by ~7~3~
a tran5verse pin 49, to an actuat.i~g mechanism 50 which may be either manually, electrically or hydraulically operated to effect a selective shifting of the pilot spool 30 in either direction f.rom the aforesaid neutral position. In the e~ample illustrated in these drawings, the actuating mechanism sn comprises a pair of axially spaced solenoid coils 51 and 52 which respectively coopera-te with a ferro-magnetic core 53 which is secured to a shaft 54, which in turn is secured to the pilot spool 30 by the 10 transverse pin 49. An external housing 55 is provided fQr mounting solenoid coils 51 and 52 and also provides a threa~ed mounting for adjustable end stops 56 and 57 which permit selective ad~ustment of the amount of axial displacement of the pilot spool 30 to be effected through the selec-tive actuation oE either solenoid coil 51 or sol~noid coil 52.
As will be understood by those skilled in the art, whenever actuation of the ~our-way valve 1 is desired to effect the operation of the double acting cylinder controlled by ~uch valve in a particular directionl an electrical signal will be applied to ei~r solenoid coil 51 or sole~oid coil 5~ to selectively shift the pilot spool 30 in one or the other axlal dir~ction to effec~ the required shifting of the ~lve spool 20 in the direction required to ef~ect the connectivn of the fluid pressure port 13 wit~
the corr~ct side vf the double acting cylinder (not shown) and one o~ the exhaust or re-turn ports 12 or 14 w.ith the other~slde of such double acting cylinderO
The operation of the aforedescrib~d device may be best understood by r~ferring to the enlarged scale drawings of Figures 2, 3 and 4. In Figure 2, it .is assumed that an appropriate electrical signal has been applied to the actuating m~chanism 50 to effect the shifting of the pilot spcol 30 to the right. This acti.on removes the central ~alving shoulder 32 of the pilot valve 30 from its position of alignment with the radial port 26 and permits fluid pressure to flow from the fluid pressure outlet connected 3~
port 13 through the annular recess 31~ and into the ~luid passage 30a provided in the pilot spool 30 to apply fluid pressure to the chamher A defined between the annular sealing mechanism 28 and the end face of the main valve spool 20. Concurrently, exhaust pressure is established in the fluid pressure chamber ]3 defined between the opposite end face of -the main valve spool 20 and the annulax fluid sealing mechanism 29 by virtu~ of fluid flow from the exhaust or return port 14 through the internal fluid passage 30b in the pilot spool 30. Thus a fluid pressure differential is applied to ~he main spool 20 in the direction to cause such main spool to precisely follow the axial displacement of the p:ilot spool 30, as illustrated in Figure 3.
Referring now to Figur,? 3, wherein the main spool 20 is shown in its axially shi:fted position, it should be first noted that the mairl spool 20 resumes its neutral position relative to the pilot spool 30 and hat the fluid pressures on the opposite end faces of the main spool 20 in the chambers A and B are again balancedO Additionally~
however, the fluid pressure port 13 which connects with the outlet side o:E the fluid pr,~ssure source (not shown~ is now connected directly to the radial pOIt 16 leadi.ng to one side of the double acting cylinder (not shown) while the other side of such cylinder is connected through por-t 15 to the exhaust or return port 12 which is connected to the inlet side of the fluid pressure source. Thus the double acting cylind~r controlled :by the four way valve will have been shifted in t,he desired direction, Referring now to Figure 4, there is shown the position of the main spool 20 and th~? pilot spool 30 when shifting of the double acting piston to be controlled is required in the opposite directi.on. f~ere, the pilot spool 30 is firs~
moved to the left by the actuating mechanism 50, and the main spool 20 immediately follows such axial movement by virtue of the establishment of a fluid pressure 1() 3~
differential in the chambers A and B at the opposite ends of the valve spool 20 to cause it to follow the pilot spool and again resume a neutral position with respect to the pilot spool 30. In this left hand position, the port 15 is now connected to the outlet side of the fluid pressure source while the port 16 is connected to the return or inlet side of the fluid pressure souree through port 14.
Thus~ operation of the valve to be controlled in the opposite direction has been achieved.
Under either conditions of operation, upon removal of the controlling signal from the actuating mechanism 50, resulting in the de~energization of the solenoid coil 51 or S2 as the case may be, the pilot spool 30 is returned to lts original neutral position by the centering spring 46. This causes the main spool 20 to follow the pilot ~pool 30 through the establishm~nt of differential pressures in the chambers A and B and the entire valving unit returns to the neutral or inop~rative po~ition illustrated in Figure 1.
The fact that the main spool 20 exactly follows the axial displacement movements of the pilot spool 30 may be advantageously utili2ed to produce a throttling control of the amount of fluid to be transmitted to the double acting cylinder to be controlled by the valve l. Thus, ad~ustment of the threaded end ~top~ 56 and 57 provided in -the pilot spool actuating mechanism 50 will limit the axial movement of pilot spool 30 and will correspondingly limit the following movement of the main valve spool 20. This movement may be reduced to the extent that a throttling action is imposed on the fluid passages established by the axial shifting of the main valve spool 20, thus limiting the amount of fluid flow to the cylindex to be controlled.
HPnce, a four-way valve incorporating this invention not only permits the selective actuation of a double acting cylinder in either direction, but also permits adjustment of the rate of flow of 1uid to said cylinder to control ~ , .
3~
the rate of movement of the cylinder in the desired direction.
Although the inventioll has beeIl described in terms of specified embodiments which are set forth in detail, it should be understood that this is by illustration only and ~hat the invention is not necessarily limited thereto, since alternative embodiments and operating techniques will become apparent to those skilled in the art in view of the disclosure. Accordingly, modifications are contemplated which can be mad~ without departing from the spirit of the described invention.
The invention relates ~o a four-way spool type valve for controlling the respective application of fluid pressure and ~xha~st pressure to opposite sides of a double acting piston disposed within a cylinder r wherein the pilot valve for controlling the moveme~s of the v~lve spool is contained within an axial bore extending through the valve spool.
A four-way hydraulic valve or the selective application of fluid pressure and exhaust pressure xespectively to opposite sides of ~ double acting piston-cylinde.r combination has been heretofore utiliz.ed in many industrial applications. Where substantial fluid pressures are invol~ed, the four-way valve generally has to be of substantial si2e in order to withstand the pressures applied to the double acting cylinder. Such control valve has generally taken the form of an outer housing containing axially spaced radial ports which are ~espectively connectable to the pressure and exhaust side of a fluid pressure souxce and the opposite sides of th~ cylinder containing the double acting piston. The flow of fluid through the proper ports is norn~ally controlled by an axially shiftable spool mounted within the ported housing and having external sealing elements for effecting the required separation of the various ports in accordanc~ with the ax.ial position of the spool relative to such ports~ To effect the xapid shifting of the valve spool in order to expedite the application of proper control pressures to the double acting cylinder, it has been common to apply diferentlal fluid pressures to the ends of the spool through th~ m~dium of a relatively small pilot valve ? which .~ ~
is operated either manually or hy an el.ectrical or hydraulic actuator. The employment o a separate pilot valve inherent-ly involves the utilization of separate fluid pressure con--duits leading from the pilot valve to the main spool type valve, with an attendant increase in total bulk of the val-ving packagef increased cost of assembly, arld increased risk of failure of the valve du0 to rupture of the exposed ex-~ernal piping.
There is a need, there~ore, for a four-way spool type hydraulic valve employing a pilot valve to efect -the control movements o~ the spool of the four-way valve~ where-in the pilot valve may be incorporated as an internal part of the spool valve and any external conduits connecting the pilot ~alve to the spool valve may be elimlnated.
Moreover, there is often a need for convenient adjustment of the speed of operation of a double acting cv-linder controlled by a four-way spool valve.
Accordingly, the lnvention provides a ~al~e for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamb~r incorporating a fluid pressure responsiva piston, comprising, in combina-tion, a hollow housing having an axially spa~ed pair of first radial ports Gonnectable respectively to the fluid pressure chamber on opposite sides o~ the piston, an axially spaced pair of second radia~ ports connectable respectively with the inlet and outlet of the fluid pressure source, the first ports being respectively axially adjacent the second ports, a valve spool axially slidable in the bore of -~he hollow housing, the valve spool hav.ing axially spaced external seal elements cooperable with the housing bore and recessed ex ternal surfases intermediate the external seal elements, whereby in a neutral axial position of the spool no fluid flow occurs~ in one axial position of ~he spool away Erom the neutxal position, pressurized fluid flows through the pair of first ports in one direction, and in a second axial position of the spool in the opposite direction from the neutr~l position the flow of pressurized fluid through the r~
3~1 2a pair of first ports is r~versed, the valve spool having an axial bore and radial ports connecting the valve spool bore with the recessed external surfacesl a pilot spool axially shiftably mounted in the valve spool bore, external sPaling means on the pilot spool respectlvely sealing each of the radial ports in a neutral position of -the pilot spool rela-tive to ~he valve spooll a pair of axially extending pass-ages r~spectively exte~diny rom ~ region intermediate -the external sealing means on th~ pilot spool to an axial end region of the hollow housing, and means ~or axially dis-placing the pilot spool from its said neutral position, thereby applying pressured fluid to one end of the valve spool to axially shi~ same from its said neutral positionO
The invention contemplates the provision of an axial bore in the spool of an otherwise conventional Eour way hydraulic spool valve. Within such axial bore, there is slidably mounted a pilot spool element. One end of the pilot spool element extends axially out of the valve spool bor~ and is connected to means Eor eEfecting an axial dis-placement of the pilot spool relative to the main valve spool.Such means may, or example, comprise a pa~r of solenoids surrounding a magnetic core element which is secured to the pilot valve so that selective energization of one of the ~olenoids effe¢ts the shifting of the pilot spool in one or ths other axial direction.
A plurality of radial ports are provided in the main valve spool respectively connecting the valve spool bore with two conduits in the main valve housing which are connectea to the return side of the hydraulic pressure 3~
source and with a single conclui~ connected to the pressure side of the hydraulic pressure source. The pilot spool is provided with a~ially spaced sealing shoulders which, in the neutral position of the pilot spool relative to the main valve spool, respective]y close each of the radial ports in the main valve spool. The pilot spool is noxmally held in such neutral position by a centering spring.
Axial displacement of the pilot spool by the external means provided for such purpose effects the connection of the fluid pressure conduit to one and of the main valve spool and the exhaus-t or return fluid conduit to the other end of such spool. Such fluid pressure differential effects a shiftin~ of the ma:Ln spool to effect the connectioll of one side of the double acting cylinder controlled by the four-way valve to the pressure source while the other side is connecked to the exhaust or return fluid conduit, hence effecting the actuation of the double acting cylinder. Such movement of the main spool valve constitutes an exact following movement ~f the shifting of the pilot spool so that these two elements again resume a neutral position relative to each other where the fluid pressures on the opposite ends of the main valve spool are again balanced, and the main valve spool remains in its described energi~ing conditi~n until the pilot spool is shifted in the opposite directlon by its actuating means.
~ 'he movement of the pilot spool past its neutral position in an opposite dirertion effects a reversal of the application of f1uid pressure and exhaust pressure xespectively to the opposite ends of the main valve spool, and thus shifts the main val-~e spool in a dir~ction opposite to that previously ~escribed. Such axial shifting movement of the main valve spool reverses the application of fluid pressure and exhaust pressure to the sldes of the double acting cylinder and thus effects a reversal of the operation of such cylinder. Again, -the movement of the main valve spool exactly follcws the movement of the pilot ~7~
valve and it again assumes the neutral position with respect to the pilot valve wherein the ~luid pressure operating on the ends of the main valve spool are equali~ed.
Whenever the actuatins force is removed from ~he pilo-t spool, the pilot spool r~turns to its original neutral posi-tion through the action of the centering spring, an~ the spool of the our-way valve is returned to its initial posi-tion wherein no fluid pressure is applied to the double acting cylind~r controlled by such valve.
The fact that the main spool exactly follows the axial movements of the pilot spool p~rmits a throttling action to he imposed on fluid flow to the controlled cylinder sim-ply by adjusting the limits of movement of the pilot spool.
Further objects and advantages of the invention will be readily apparent to those skilled in the art from the following detailed description, taken in conjunction with the annexed sheets of drawings on which is shown a preferred embodiment of the invention.
Embodiments of the invention will now be described, by way of example, with reference to the accompanying draw-in~s in which:
Figure 1 is a vertical sectional view of a four-way hydraulic valve incorporating an embodiment of this invention, with the elements of the valve shown in their neutral or de-energizing positions.
Figure 2 is an enlarged scale view of a portion of Figure 1, buk illustrating the position of the pilot spool when it is axially shifted in one direction by the actuating solenoîd.
Figure 3 is a view similar to Figure 2 bu~ illustra-ting the position ass~uned by the maln valve spool in response to the axial shifting of the pilot spool.
Figure 4 is a view similar to Figure 3 but showing the positions assumed by the pilot spool and the main spool valve in response to an actuation of the pilo-t spool in an opposite direction.
'~
7~3~
Figure 5 is a fragmerl~ary elevational view of the ported portion 3f the valve sleeve housing.
Keferring to Figure 1, there is shown a complete four-way spool type valve 1 embodying this invention. Such valve comprises an outer main housing 10 defining a central bore 11 which is open only at one end. Housing 10 is provided wi~h a plurality of axially spaced radial port~
10 12, 13, 14, 15, 16 and 17, each extending from the periphery of the housing 10 into communication with the bore 11. Each port i5 internally threaded to receive a correspondingly threaded end of a conduit in the case o~
ports 12 through 16, and to receive a plug in -the case o~
port 17.
Ports 15 and 16 are respectively adapted for connection to opposite ends of a conventional double acting cylinder~ (nQt shown) i.e., a cylinder ha~ing a piston medially disposed therein and fluid pressure chambers disposed on each side of such piston so that the application of a fluid pressure differential -to opposite sides o the piston produces a cor.responding movemPnt of the piston in the cylinder. Port 13 is ~dapted for connection to the pressured outlet side of a fluid pressure source ~not shown) an~ ports 12 and 14, which are respectively axially spaced on oppos~te si.des of port 13 are adapted for connection to the return or inl~ of the fluid pressure source. Port 17 is located adjacent the extreme innex end of the housing bore 11 and is provided solely for the purpQse of dxaining the val~e 1 by removal of a plug therefrom ~not shown)O
While the housin~ 10 could be employed alon~ ~o directly mount an axially reciprocable valve spool 20 therein, this invention preferably utilizes an intermediate sleève housing 18 which is fixedly and sealably mounted within the bore 11 of the outer housing 10~ Sleeve 18 may 3~3 thus be economically fabric~te~ from a metal having better anti-friction characteristics for the mounting of the main valve spool 20 therein. Valve sleeve 18 is provided with radial ports 18a, 18b, 18c, 18d, and 18e respectively alisn`able with the ports 12, 13, 14, 15, and 16 provided in the main valve housing 10. O-ring seals 19 ~Fig~ 5) are mounted in clrcular slots cut around the exterior perimeter of the res~ective ports 18a-18e to effect a sealing engagement between bore 11 of the outer valve housing 10 and the inner sleeve housin~l 18. Sleeve housing 18 is secured in its inserted posi.tion in ~he main housing bore 11 by a plate 9 which is cer,trally apertured to abut a shoulder 18 f provided on the sleeve housing 18 and is secured to the end face of t:he main valve housing 10 by one or more bolts 9a. An O-rincl seal 18g is mounted in the outer end of sleeve housing lB and effects a further seal between the sleeve housing 18 and the bore 11 of the main housing 10.
Within the polished bore 18h ~f the housing sleeve 18, there is mounted a valve spc~ol 20 for axially slidable movements. Spool 20 is provided with axially spaced external sealing shoulders ~'1, 22, 23 and 24. Between the adjacent shoulders the exte~-nal surface of the valve spool is recessed, as indicated al 21a, 22a, and 23aO In a neutral or inoperative posil:ion of the valve spool 20 with respect to the ports 12 through 16, the sealing shoulders are disposed so as to isolal:e the various ports from each other and prevent all fluid flow through the valve 1 to the controlled cylinderO The annular recesses 21a, 22a, and 23a are in turn respectivel~y connected to a ~ore 20a extending through the valve spool 20 by a plurality of radial ports 25, 26 and 27.
The extent of axial di:placement of valve spool 20 relative to housing sleeve :L8 is respectively limited in each direction by annular seal structures 28 and 29 which are respectively held in a :~ix~d position within the bor~
.
3~
18h of housiny sleeve 18 by ('-rings 28a and 29a respectively.
In accordance with this invelltion, a pilot spool 30 is mounted for axial movements within the axial bore 20a of the spool v~lve 20 and is sealingly eng~ged by seal elements 28b and 29b provid~d in the annular seal structures 28 and 29. Pilot spool 30 is provided with ~xially spaced sealing portions 31~ 32 and 33, which, in the neutral position of the pilot spool 30 relative to ~he valve spool 20 are respectively disposed in overlying relationship to the radial ports 25~ 26 and 27 when the pi.lot spool 30 is disposed in a neutral position with respect to the main spool valve 20. External recesses 31a and 32a are formed intermediate shoulders 31~ 32 and 33.
Pilot valve 30 is held in the aforesaid neutral positi.on by a centering spring mechanism 40 comprising an annular housing 41 which is externally threaded into internal threads 18k pLovided in the end of the housing sleeve 13. The spring centering housing 41 defines two axially spaced internally projecting shoulders 41a and 41b which respectively define stops for annular spring seats 42 and 43, which are in abuttment with C-rings 44 and 45 secured to the pilot spool 30. A spring 46 between spring seats 42 and 43 resiliently maintains the pilot spool 30 in its afores~id neutral position relative to the main valve spool 20.
In the neutral position of the pilot spool 30, a pair o:E generally U-shaped fluid passag~s 30a and 30b provided in the body of the pilot spool 30 respectively extend from a position axially inward from the recessed poxtions 31a and 32a of the pilot spool 30 to two outlets on the pilot spoGl which are respectively disposed within enlarged counter bores 20c and 20d provided .in the ends of the bore 20a of the valve spool 20.
The end of the valve spool 30 projecting axi~lly beyond the centering spring mechanism 40 is secured, as by ~7~3~
a tran5verse pin 49, to an actuat.i~g mechanism 50 which may be either manually, electrically or hydraulically operated to effect a selective shifting of the pilot spool 30 in either direction f.rom the aforesaid neutral position. In the e~ample illustrated in these drawings, the actuating mechanism sn comprises a pair of axially spaced solenoid coils 51 and 52 which respectively coopera-te with a ferro-magnetic core 53 which is secured to a shaft 54, which in turn is secured to the pilot spool 30 by the 10 transverse pin 49. An external housing 55 is provided fQr mounting solenoid coils 51 and 52 and also provides a threa~ed mounting for adjustable end stops 56 and 57 which permit selective ad~ustment of the amount of axial displacement of the pilot spool 30 to be effected through the selec-tive actuation oE either solenoid coil 51 or sol~noid coil 52.
As will be understood by those skilled in the art, whenever actuation of the ~our-way valve 1 is desired to effect the operation of the double acting cylinder controlled by ~uch valve in a particular directionl an electrical signal will be applied to ei~r solenoid coil 51 or sole~oid coil 5~ to selectively shift the pilot spool 30 in one or the other axlal dir~ction to effec~ the required shifting of the ~lve spool 20 in the direction required to ef~ect the connectivn of the fluid pressure port 13 wit~
the corr~ct side vf the double acting cylinder (not shown) and one o~ the exhaust or re-turn ports 12 or 14 w.ith the other~slde of such double acting cylinderO
The operation of the aforedescrib~d device may be best understood by r~ferring to the enlarged scale drawings of Figures 2, 3 and 4. In Figure 2, it .is assumed that an appropriate electrical signal has been applied to the actuating m~chanism 50 to effect the shifting of the pilot spcol 30 to the right. This acti.on removes the central ~alving shoulder 32 of the pilot valve 30 from its position of alignment with the radial port 26 and permits fluid pressure to flow from the fluid pressure outlet connected 3~
port 13 through the annular recess 31~ and into the ~luid passage 30a provided in the pilot spool 30 to apply fluid pressure to the chamher A defined between the annular sealing mechanism 28 and the end face of the main valve spool 20. Concurrently, exhaust pressure is established in the fluid pressure chamber ]3 defined between the opposite end face of -the main valve spool 20 and the annulax fluid sealing mechanism 29 by virtu~ of fluid flow from the exhaust or return port 14 through the internal fluid passage 30b in the pilot spool 30. Thus a fluid pressure differential is applied to ~he main spool 20 in the direction to cause such main spool to precisely follow the axial displacement of the p:ilot spool 30, as illustrated in Figure 3.
Referring now to Figur,? 3, wherein the main spool 20 is shown in its axially shi:fted position, it should be first noted that the mairl spool 20 resumes its neutral position relative to the pilot spool 30 and hat the fluid pressures on the opposite end faces of the main spool 20 in the chambers A and B are again balancedO Additionally~
however, the fluid pressure port 13 which connects with the outlet side o:E the fluid pr,~ssure source (not shown~ is now connected directly to the radial pOIt 16 leadi.ng to one side of the double acting cylinder (not shown) while the other side of such cylinder is connected through por-t 15 to the exhaust or return port 12 which is connected to the inlet side of the fluid pressure source. Thus the double acting cylind~r controlled :by the four way valve will have been shifted in t,he desired direction, Referring now to Figure 4, there is shown the position of the main spool 20 and th~? pilot spool 30 when shifting of the double acting piston to be controlled is required in the opposite directi.on. f~ere, the pilot spool 30 is firs~
moved to the left by the actuating mechanism 50, and the main spool 20 immediately follows such axial movement by virtue of the establishment of a fluid pressure 1() 3~
differential in the chambers A and B at the opposite ends of the valve spool 20 to cause it to follow the pilot spool and again resume a neutral position with respect to the pilot spool 30. In this left hand position, the port 15 is now connected to the outlet side of the fluid pressure source while the port 16 is connected to the return or inlet side of the fluid pressure souree through port 14.
Thus~ operation of the valve to be controlled in the opposite direction has been achieved.
Under either conditions of operation, upon removal of the controlling signal from the actuating mechanism 50, resulting in the de~energization of the solenoid coil 51 or S2 as the case may be, the pilot spool 30 is returned to lts original neutral position by the centering spring 46. This causes the main spool 20 to follow the pilot ~pool 30 through the establishm~nt of differential pressures in the chambers A and B and the entire valving unit returns to the neutral or inop~rative po~ition illustrated in Figure 1.
The fact that the main spool 20 exactly follows the axial displacement movements of the pilot spool 30 may be advantageously utili2ed to produce a throttling control of the amount of fluid to be transmitted to the double acting cylinder to be controlled by the valve l. Thus, ad~ustment of the threaded end ~top~ 56 and 57 provided in -the pilot spool actuating mechanism 50 will limit the axial movement of pilot spool 30 and will correspondingly limit the following movement of the main valve spool 20. This movement may be reduced to the extent that a throttling action is imposed on the fluid passages established by the axial shifting of the main valve spool 20, thus limiting the amount of fluid flow to the cylindex to be controlled.
HPnce, a four-way valve incorporating this invention not only permits the selective actuation of a double acting cylinder in either direction, but also permits adjustment of the rate of flow of 1uid to said cylinder to control ~ , .
3~
the rate of movement of the cylinder in the desired direction.
Although the inventioll has beeIl described in terms of specified embodiments which are set forth in detail, it should be understood that this is by illustration only and ~hat the invention is not necessarily limited thereto, since alternative embodiments and operating techniques will become apparent to those skilled in the art in view of the disclosure. Accordingly, modifications are contemplated which can be mad~ without departing from the spirit of the described invention.
Claims (15)
1. A valve for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamber incorporating a fluid pressure responsive piston, comprising, in combination: a hollow housing having an axially spaced pair of first radial ports connectable respectively to said fluid pressure chamber on opposite sides of said piston, an axially spaced pair of second radial ports connectable respectively with said inlet and outlet of the fluid pressure source; said first ports being respectively axially adjacent said second ports; a valve spool axially slidable in the bore of said hollow housing;
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and means for axially displacing said pilot spool from its said neutral position, thereby applying pressured fluid to one end of said valve spool to axially shift same from its said neutral position.
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and means for axially displacing said pilot spool from its said neutral position, thereby applying pressured fluid to one end of said valve spool to axially shift same from its said neutral position.
2. A valve for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamber incorporating a fluid pressure responsive piston, comprising, in combination: a hollow housing having an axially spaced pair of first radial ports connectable respectively to said fluid pressure chamber on opposite sides of said piston, an axially spaced pair of second radial ports connectable respectively with said inlet and outlet of the fluid pressure source; said first ports being respectively axially adjacent said second ports; a valve spool axially slidable in the bore of said hollow housing;
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position, the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and means for axially displacing said pilot spool in either direction from its said neutral position thereby selectively applying pressured fluid to one end or the other of said valve spool to selectively axially shift same in opposite directions front its said neutral position.
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position, the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and means for axially displacing said pilot spool in either direction from its said neutral position thereby selectively applying pressured fluid to one end or the other of said valve spool to selectively axially shift same in opposite directions front its said neutral position.
3. The apparatus of claim 1 or 2 plus resilient means opposing the displacement of said pilot spool in either direction from said neutral position.
4. The apparatus of claim 1 or 2 wherein said valve spool shifts in the same direction as said pilot spool, thereby restoring the neutral position of said pilot spool relative to said valve spool.
5. The apparatus of claim 1 or 2 wherein said valve spool comprises a tubular element and fur her comprising annular sealing assemblies respectively mounted between the outer ends of said pilot spool and said axial bore of said housing to define fluid pressure chambers respectively cooperating with the end faces of said valve spool to apply fluid pressure forces thereto.
6. The apparatus of claim 1 or 2 further comprising a conduit connecting housing having a cylindrical bore for sealingly mounting said hollow housing, and internally threaded, conduit receiving, radial ports respectively aligned with said hollow housing ports.
7. The apparatus of claim 1 wherein said means for axially displacing said pilot spool comprises a solenoid.
8. The apparatus of claim 2 wherein said means for axially displacing said pilot spool in either direction from its said neutral position comprises solenoid core means secured to said pilot spool and a pair of axially spaced coils cooperable with said solenoid core to respectively shift same in opposite directions upon respective energization of said solenoid coils.
9. A valve for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamber incorporating a fluid pressure responsive piston, comprising, in combination: a hollow housing having an axially spaced pair of first radial ports connectable respectively to said fluid pressure chamber on opposite sides of said piston, an axially spaced pair of second radial ports connectable respectively with said inlet and outlet of the fluid pressure source; said first ports being respectively axially adjacent said second ports; a valve spool axially slidable in the bore of said hollow housing;
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and adjustable means for axially shifting said pilot spool a predetermined distance from its said neutral position;
whereby said valve spool shifts the same amount and direction as said pilot spool to restore the neutral position of said pilot spool relative to said valve spool and establish a flow rate thru said housing ports that is a function of said axial shifting distance of said pilot valve.
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means on said pilot spool to an axial end region of said hollow housing;
and adjustable means for axially shifting said pilot spool a predetermined distance from its said neutral position;
whereby said valve spool shifts the same amount and direction as said pilot spool to restore the neutral position of said pilot spool relative to said valve spool and establish a flow rate thru said housing ports that is a function of said axial shifting distance of said pilot valve.
10. A valve for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamber incorporating a fluid pressure responsive piston, comprising, in combination: a hollow housing having an axially spaced pair of first radial ports connectable respectively to said fluid pressure chamber on opposite sides of said piston, an axially spaced pair of second radial ports connectable respectively with said inlet and outlet of the fluid pressure source; said first ports being respectively axially adjacent said second ports; a valve spool axially slidable in the bore of said hollow housing;
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction; and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means, on said pilot spool to an axial end region of said hollow housing;
and adjustable means for axially shifting said pilot valve a predetermined distance in either direction from its said neutral position; whereby said valve spool shifts the same amount and direction as said pilot spool to restore the neutral position of said pilot spool relative to said valve spool and establish a flow rate thru said housing ports that is a function of said axial shifting distance of said pilot valve.
said valve spool having axially spaced external seal elements cooperable with said housing bore and recessed external surfaces intermediate said external seal elements, whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position, pressurized fluid flows through said pair of first ports in one direction; and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore;
external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said external sealing means, on said pilot spool to an axial end region of said hollow housing;
and adjustable means for axially shifting said pilot valve a predetermined distance in either direction from its said neutral position; whereby said valve spool shifts the same amount and direction as said pilot spool to restore the neutral position of said pilot spool relative to said valve spool and establish a flow rate thru said housing ports that is a function of said axial shifting distance of said pilot valve.
11. A valve for selectively connecting the inlet and outlet of a fluid pressure source to a fluid pressure chamber incorporating a fluid pressure responsive piston, compris-ing, in combination: a hollow housing having an axially spaced pair of first radial ports connectable respectively to said fluid pressure chamber on opposite sides of said piston, an axially spaced pair of second radial ports con-nectable respectively with said inlet and outlet of the fluid pressure source; said first ports being respectively axially adjacent said second ports; a valve spool axially slidable in the bore of said hollow housing; said valve spool having axially spaced external seal elements cooper-able with said housing bore and recessed external surfaces intermediate said external seal elements whereby in a neutral axial position of said spool no fluid flow occurs, in one axial position of said spool away from said neutral position pressurized fluid flows through said pair of first ports in one direction, and in a second axial position of said spool in the opposite direction from said neutral position the flow of pressurized fluid through said pair of first ports is reversed; said valve spool having an axial bore and radial ports connecting said valve spool bore with said recessed external surfaces, a pilot spool axially shiftably mounted in said valve spool bore; external sealing means on said pilot spool respectively sealing each of said radial ports in a neutral position of said pilot spool relative to said valve spool; a pair of axially extending passages respectively extending from a region intermediate said exter-nal sealing means on said pilot spool to an axial end region of said hollow housing; and adjustable means for axially shifting said pilot valve a predetermined distance in either direction from its said neutral position, said adjustable means including a solenoid core secure to said pilot spool, a first solenoid coil axially spaced from a second solenoid coil, said first and second solenoid coils cooperable with said solenoid core to respectively shift said solenoid core in opposite directions upon respective energization of said solenoid coils, a first threadably adjustable stop means associated with said first solenoid coil for limiting the axial movement of said solenoid core and said pilot spool in one direction with said first solenoid coil is energized and a second threadably adjustable stop means associated with said second solenoid core for limiting the axial move-ment of said solenoid core and said pilot spool in an oppo-site direction when said second solenoid is energized; where-by said valve spool shifts the same amount and direction as said pilot spool to restore the neutral position of said pilot spool relative to said valve spool and establish a flow rate thru said housing ports that is a function of said axial shifting distance of said pilot valve.
12. The apparatus of claim 9, or 10 or 11 plus resi-lient means opposing the displacement of said pilot spool in either direction from said neutral position.
13. The apparatus of claim 9, or 10 or 11 wherein said valve spool comprises a tubular element and further comprising annular sealing assemblies respectively mounted between the outer ends of said pilot spool and said axial bore of said housing to define fluid pressure chambers res-pectively cooperating with the end faces of said valve spool to apply fluid pressure forces thereto.
14. The apparatus of claim 9, or 10 or 11 further comprising a conduit connecting housing having a cylindrical bore for sealingly mounting said hollow housing, and in-ternally threaded, conduit receiving, radial ports respective-ly aligned with said hollow housing ports.
15. The apparatus of claim 9 wherein said adjustable means for axially shifting said pilot spool a predetermined distance comprises a solenoid coil; a ferro-magnetic core element secured to said pilot spool and cooperable with said solenoid coil; and threadably adjustable stop means limiting the axial movement of said pilot spool produced by said solenoid coil.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/439,057 US4526201A (en) | 1982-11-04 | 1982-11-04 | Four-way valve with internal pilot |
| US439,057 | 1995-05-08 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1197438A true CA1197438A (en) | 1985-12-03 |
Family
ID=23743107
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000440343A Expired CA1197438A (en) | 1982-11-04 | 1983-11-03 | Four way valve with internal pilot |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US4526201A (en) |
| JP (1) | JPS59131073A (en) |
| AU (1) | AU565284B2 (en) |
| CA (1) | CA1197438A (en) |
| DE (1) | DE3340001A1 (en) |
| FR (1) | FR2535818A1 (en) |
| GB (1) | GB2129528B (en) |
Families Citing this family (28)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4611632A (en) * | 1985-05-06 | 1986-09-16 | Imperial Clevite Inc. | Hydraulic solenoid valve structure |
| GB8713304D0 (en) * | 1987-06-06 | 1987-07-08 | Lucas Ind Plc | Fluid control valve |
| DE3925300A1 (en) * | 1989-07-31 | 1991-02-14 | Linde Ag | ELECTRO-HYDRAULIC SIGNAL CONVERTER |
| US5520217A (en) * | 1993-08-11 | 1996-05-28 | Sun Hydraulics Corporation | Directional valve |
| US5806565A (en) * | 1994-02-04 | 1998-09-15 | Microhydraulics Inc. | Hydraulic valves |
| DE19729935B4 (en) * | 1997-07-12 | 2006-11-16 | Hydraulik-Ring Gmbh | Hydraulic cartridge valve, in particular for a hydraulic camshaft adjustment on a motor vehicle engine |
| US6481463B1 (en) * | 1999-05-21 | 2002-11-19 | Parker-Hannifin Corporation | Control valve with mechanical feedback and method for controlling fluid flow |
| US6431957B1 (en) | 2000-01-25 | 2002-08-13 | Parker-Hannifin Corporation | Directional flow control valve with recirculation for chemical-mechanical polishing slurries |
| GB2374130B (en) * | 2001-04-04 | 2004-09-29 | Delphi Tech Inc | A reversing valve for a motor vehicle air conditioning system |
| US6857423B2 (en) * | 2003-02-11 | 2005-02-22 | Paul Garfield Jong | Paintball marker and kit of parts therefor |
| US7070161B2 (en) * | 2003-09-11 | 2006-07-04 | Continental Hydraulics | Proportional directional control valve with a magnetic positioning sensor |
| GB2413616B (en) * | 2004-04-26 | 2007-02-14 | Evolve Paintball Ltd | Pneumatic spool valve |
| DE102010050325A1 (en) * | 2010-11-05 | 2012-05-10 | Parker Hannifin Gmbh | Hydraulic control valve with a arranged in the hollow valve spool four control edges having pilot piston |
| DE102010050323A1 (en) * | 2010-11-05 | 2012-05-10 | Parker Hannifin Gmbh | Hydraulic control valve with a arranged in the hollow valve spool control piston |
| US9217341B2 (en) * | 2013-08-15 | 2015-12-22 | Caterpillar Inc. | Lubrication system for tool |
| JP5938839B2 (en) * | 2014-02-10 | 2016-06-22 | Smc株式会社 | Solenoid pilot spool valve |
| US9404599B2 (en) * | 2014-03-12 | 2016-08-02 | Flextronics Automotive Inc. | Dual/variable gain oil pump control valve |
| GB201420289D0 (en) * | 2014-11-14 | 2014-12-31 | Blagdon Actuation Res Ltd | Improvements in and relating to servo valves |
| DE102015110664A1 (en) * | 2015-07-02 | 2017-01-05 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Changeover valve and internal combustion engine |
| CN107420376B (en) * | 2017-05-10 | 2023-04-07 | 中国人民解放***箭军工程大学 | Built-in pilot valve spool vibration displacement signal on-line measuring device |
| DE102018115701A1 (en) * | 2018-04-30 | 2019-10-31 | Tries Gmbh & Co. Kg | Valve unit with two pilot valves and two main valves |
| US10557483B1 (en) * | 2018-09-18 | 2020-02-11 | Sun Hydraulics, Llc | Electrohydraulic valve normally operating in pressure relief mode and configured to operate in ventable mode when actuated |
| US10774853B2 (en) * | 2018-09-18 | 2020-09-15 | Sun Hydraulics, Llc | Electrohydraulic valve normally operating in fluid flow-blocking mode and configured to operate in pressure relief mode when actuated |
| US10570932B1 (en) * | 2018-09-18 | 2020-02-25 | Sun Hydraulics, Llc | Electrohydraulic valve normally operating in pressure relief mode and configured to block fluid flow when actuated |
| DE102018216831A1 (en) * | 2018-10-01 | 2020-04-02 | Robert Bosch Gmbh | Control device for pump pressure and volume flow with concentric control spools |
| US10775812B1 (en) * | 2019-01-22 | 2020-09-15 | Sun Hydraulics, Llc | Inverse proportional pressure relief valve |
| US10683879B1 (en) * | 2019-01-22 | 2020-06-16 | Sun Hydraulics, Llc | Two-port electrohydraulic counterbalance valve |
| US20220333835A1 (en) * | 2021-04-16 | 2022-10-20 | Carrier Corporation | System and method for controlling a flow of refrigerant in a reversing valve |
Family Cites Families (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1125825A (en) * | 1912-06-27 | 1915-01-19 | Allis Chalmers Mfg Co | Distributing-valve. |
| US2771907A (en) * | 1949-01-29 | 1956-11-27 | Joy Mfg Co | Pilot controlled piston type reversing valve |
| US2600348A (en) * | 1949-12-30 | 1952-06-10 | Gen Electric | Two-stage hydraulic control valve |
| US2655940A (en) * | 1950-01-09 | 1953-10-20 | North American Aviation Inc | Time-modulated two-stage hydraulic valve |
| US2952246A (en) * | 1957-07-12 | 1960-09-13 | Int Basic Economy Corp | Valve |
| US2954050A (en) * | 1957-12-23 | 1960-09-27 | Honeywell Regulator Co | Control valve |
| US3060969A (en) * | 1960-02-24 | 1962-10-30 | Alkon Products Corp | Hydraulic valve |
| DE1245665B (en) * | 1963-01-23 | 1967-07-27 | Erich Herion | Control valve |
| GB1041074A (en) * | 1963-04-30 | 1966-09-01 | Walter Donald Ludwig | Two-position, pilot-operated, valve |
| DE1450538A1 (en) * | 1964-02-18 | 1968-11-14 | Herion Erich | Multi-way switch valve |
| US3412971A (en) * | 1966-03-03 | 1968-11-26 | Armstrong Cork Co | Electrically-controlled valve apparatus and control circuit suitable for use therein |
| US3554234A (en) * | 1967-12-22 | 1971-01-12 | Westinghouse Air Brake Co | Hydraulic directional control valve device |
| US3603348A (en) * | 1969-07-31 | 1971-09-07 | Mosier Ind Inc | Valve improvements |
| CA951224A (en) * | 1971-06-25 | 1974-07-16 | Applied Power Industries | Flexible cable hydraulic control means |
| US3918488A (en) * | 1971-06-30 | 1975-11-11 | Komatsu Mfg Co Ltd | Control valves for steering clutches and brakes |
| US3874405A (en) * | 1973-08-24 | 1975-04-01 | Moog Inc | Multiple tow-stage electrohydraulic servovalve apparatus |
| US3870074A (en) * | 1974-04-26 | 1975-03-11 | Deere & Co | Valve for controlling a reversible, rotary hydraulic motor |
| US3924656A (en) * | 1974-04-26 | 1975-12-09 | Deere & Co | Direction control valve having float mode |
| US4067357A (en) * | 1974-06-14 | 1978-01-10 | Herion-Werke Kg | Pilot-operated directional control valve |
| DE2506864A1 (en) * | 1975-02-18 | 1976-08-26 | Schneider Co Optische Werke | DIRECTIONAL VALVE |
| JPS5815707Y2 (en) * | 1976-08-26 | 1983-03-30 | 焼結金属工業株式会社 | Pilot type directional valve |
| JPS5833950B2 (en) * | 1978-12-07 | 1983-07-23 | 豊興工業株式会社 | fluid control valve |
| US4276896A (en) * | 1979-11-05 | 1981-07-07 | Deere & Company | Flow control valve assembly with integrated torque and flow divider control |
-
1982
- 1982-11-04 US US06/439,057 patent/US4526201A/en not_active Expired - Fee Related
-
1983
- 1983-11-03 CA CA000440343A patent/CA1197438A/en not_active Expired
- 1983-11-03 AU AU20937/83A patent/AU565284B2/en not_active Ceased
- 1983-11-04 GB GB08329571A patent/GB2129528B/en not_active Expired
- 1983-11-04 FR FR8317555A patent/FR2535818A1/en active Granted
- 1983-11-04 DE DE19833340001 patent/DE3340001A1/en not_active Withdrawn
- 1983-11-04 JP JP58207338A patent/JPS59131073A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE3340001A1 (en) | 1984-05-24 |
| GB8329571D0 (en) | 1983-12-07 |
| GB2129528A (en) | 1984-05-16 |
| JPS59131073A (en) | 1984-07-27 |
| AU2093783A (en) | 1984-05-10 |
| AU565284B2 (en) | 1987-09-10 |
| US4526201A (en) | 1985-07-02 |
| GB2129528B (en) | 1986-12-03 |
| FR2535818B3 (en) | 1985-03-01 |
| FR2535818A1 (en) | 1984-05-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA1197438A (en) | Four way valve with internal pilot | |
| US4643225A (en) | Pressure regulating valve | |
| US3312146A (en) | Fluid pressure jack with three stable positions | |
| US5520217A (en) | Directional valve | |
| US3783901A (en) | Electro hydraulic control unit | |
| US3267965A (en) | Pilot operated spool valve | |
| US3709257A (en) | Electro-hydraulic servomechanism | |
| US4842020A (en) | Double-solenoid single-stem four-way valve | |
| US4649957A (en) | Fluid assisted spring return for pilot operated, spool valve | |
| US3893484A (en) | Cylinder and piston valve | |
| US3028880A (en) | Fluid flow control valve | |
| US2986165A (en) | Balanced slide valve | |
| EP3406949B1 (en) | Spool valve | |
| US2953162A (en) | Compensated hydraulic valve | |
| US3339573A (en) | Flow control valve | |
| US3570523A (en) | Self-regulating reciprocator device | |
| US4513783A (en) | Directional control valve | |
| US5504409A (en) | Direct drive servovalve having two landed spool power stage | |
| US5799485A (en) | Electrohydraulic control device for double-acting consumer | |
| US3324887A (en) | Directional flow control valves | |
| GB2085123A (en) | Valve | |
| US4479514A (en) | Float positioning assembly for pilot operated valve | |
| BR8304056A (en) | DOUBLE SHIRT VALVE AND DOUBLE FILTER ASSEMBLY | |
| US3756278A (en) | Control slide valve for a hydraulic servo motor | |
| US3906835A (en) | Fluid motor control system with manual and self-cycling modes of operation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEC | Expiry (correction) | ||
| MKEX | Expiry |